US3336082A - Method and apparatus for ripping rock by sonically vibratory teeth - Google Patents

Method and apparatus for ripping rock by sonically vibratory teeth Download PDF

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US3336082A
US3336082A US402136A US40213664A US3336082A US 3336082 A US3336082 A US 3336082A US 402136 A US402136 A US 402136A US 40213664 A US40213664 A US 40213664A US 3336082 A US3336082 A US 3336082A
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bar
rock
point
vibration
vibratory
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Jr Albert G Bodine
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F5/00—Dredgers or soil-shifting machines for special purposes
    • E02F5/30—Auxiliary apparatus, e.g. for thawing, cracking, blowing-up, or other preparatory treatment of the soil
    • E02F5/32—Rippers
    • E02F5/326—Rippers oscillating or vibrating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/76—Graders, bulldozers, or the like with scraper plates or ploughshare-like elements; Levelling scarifying devices
    • E02F3/7604—Combinations of scraper blades with soil loosening tools working independently of scraper blades

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  • the invention involves my discovery that a sonically activated resonator, in combination with a tooth or point, and a high force output sonic vibration generator, has a Very unique and effective action in rock ripping.
  • the method of the invention comprises primarily the transmitting or radiation of sonic oscillation or vibration into .and through the rock material in a direction having a major component substantially parallel to the top surface Kof the rock layer.
  • the method includes rst locating a sonic radiator element, such as a tooth or point, against a shoulder of the rock layer some distance down below the top surface thereof. This distance as contemplated by the invention is of the order of a few feet, but, of course, a shallower cut may be taken if desired.
  • the sonic radiator point is then oscillated with a component of sonic vibration which is generally parallel to the top surface of 3,336,082 Patented Aug. 15, 1967 the rock, which may be either horizontal, or tilted.
  • sonic vibrations are to be transmitted through the rock, which is an elastic and frangible material, with a component of sonic wave or elastic vibration travel which is generally parallel to the top surface of the rock.
  • elastic vibration I refer to the fact that sonic waves are propagated through an elastic medium by longitudinal wave movements that comprise alternate elastic compressions and rarefactions progressing through the rock with the speed of sound in the rock media. This sonic or elastic vibration or wave propagation causes the rock to literally come apart along fracture or weakness lines which are ahead of the sonic radiating tooth or point element.
  • the top surface of the rock functions as a pressure release region, akin to or involving a sudden drop in acoustic impedance, so that a portion of the sonic wave energy transmission which works on these fracture lines tends to dive up from the sonic radiator point -up to the surface of the rock some distance ahead of the sonic radiator point.
  • the action sometimes includes a sort of a refraction phenomena, caused by a slower speed of sound nearer to the surface, which directs components of the wave transmission along upward angles lof slope.
  • acoustic impedance may be regarded as the ratio of cyclic rock pressure to vibratory velocity amplitude when a sonic wave is propagated through the rock.
  • the basic steps of the method may be described as follows: I first insert the sonic radiator point below the top surface of the rock, into engagement with a shoulder region of the rock. Such a shoulder region is maintained subsequently by the forward progress of the tooth. The next step of the method is to exert a strong forward bras force on this point, which in turn concentrates this force in a very small area on the face of the shoulder. Thls bias is typically of the order of 20,000 to 100,000 lbs., usually the practical limit of the tractor draw bar pull, so that the pressure exerted by the point on the rock is exceedingly high in pounds per square inch.
  • the bias force is of the order of magnitude of the cyclic sonic vibration force, so that the vibration radiating point stays in engagement with the rock during a substantial part of the vibration cycle, so as to be well acoustically coupled to the rock, and thereby assure transmission of strong elastic vibrations or waves into and through the rock.
  • the elastic resonator is of fairly high acoustic impedance, typically a steel bar weighing something of the order of half a ton. I nd it desirable that this resonator have a fairly high impedance, and having a substantial energy storage capacity, so as to have a substantial acoustic Q (the ratio of sonic energy stored to energy dissipated per cycle).
  • the high acoustic Q factor causes the bar, or resonator, to build up an elastic vibration to a fairly high sonic amplitude, with the result that high force or stress vibrations are transmitted into the rock.
  • the method includes the first step of engaging the point with the rock, the second step of applying to the tooth a forward bias force, in a direction having a component parallel to the surface of the rock, and a third step of sonically driving the sonic radiation point, also with a component parallel to the top surface of the rock, by means of an oscillator operated at resonance, i.e., a resonator.
  • I generate these sonic vibrations in the resonator by acoustically coupling thereto a high-forceoutput oscillatory force-generator, or sonic vibration -generator, and ⁇ operating this generator at the resonant frequencypof the resonator.
  • the basic method consists of maintaining the sonic radiator point in a region a little below the top surface of the rock, ⁇ biasing this radiator point against a shoulder surface on the rock, and resonating a resonant member which is acoustically coupled to this radiator point.
  • One important aspect of the method of the invention is the use of an elastically vibratory driving bar or shank for the radiator point that has a component of vibration which is in the direction of the lbias force and which component is generally parallel to the upper surface of the rock.
  • the resonant pattern selected for the resonator must be oriented to produce an elastic vibration having this important component of vibratory direction.
  • the method includes four requisite steps.
  • a sometimes useful additional step is to momentarily apply an upward component to the bias.
  • One preferred embodiment of the invention has the resonator in the form of a flat slab bar oriented generally vertically, so that it progresses through the rock edgewise. This wide bar is then resonated in a lateral or bending mode of standing wave vibration. The vibration is in the plane of the major lateral dimension of this flat bar.
  • the bending mode in or in parallelism with the planes of the at sides of the bar yields a fairly high elastic stiffness, so that the bar vibrates naturally at fairly high frequency, and has a fairly high acoustic impedance.
  • Such a ybar hanging free in the air, i.e., a free-free bar would normally resonate at its fundamental frequency with a substantially one-wavelength pattern.
  • This pattern has a node approximately one quarter of the distance in from each end (sometimes closer to about 0.17 of the distance) and therefore has velocity antinodes (regions of maximized vibration amplitude) at its two ends, and a velocity antinode in the center.
  • the two ends of the bar move in phase with one another, and the center portion of the bar moves in opposite phase to the two ends.
  • This step involves causing the forward bias force to be so high relative to the fairly high impedance bar that the bar impedance becomes concious of its environment. That is to say, I cause the bias force to be so high as to cause the actual impedance of the rock to become part of the reactive circuit in a special function whereby it provides almost the entire acoustic reactance of the lbottom node.
  • I cause the bias force to be so great in relation to the impedance of the bar that the high impedance normally presented by the node above the bottom quarter wavelength portion of the bar is substantially completely supplanted by the reactance of the rock itself.
  • the result is that the wave pattern becomes more nearly three quarters wavelength rather than one full wavelength.
  • the rock itself has replaced both the mass and stiffness parameters of the bottom quarter wavelength of the earlier postulated elastically vibratory free-free bar, and functions to provide almost all of the impedance function of the lowest node, so that the bar in effect behaves substantially as a clamped-free bar.
  • the bar thus vibrates substantially in a threequarter wave length pattern, with a node near the bottom, another node one-third of the length of the bar down from the top end, and antinodes at the top and two-thirds down the bar from the top.
  • a true node 1s not obtained exactly at the point but somewhat thereabove, say one-sixteenth Wavelength thereabove. There 1s thus a small vibration amplitude at the point.
  • the bar may ⁇ be mounted at its upper node, and is thus preferably arranged for pivotal movement about that node, as will be discussed hereinafter.
  • FIG. l is a top plan View of a present illustrative embodiment of the rock ripper of the invention, the view being partly in section on broken line 1 1 of FIG. 2, and the view showing also, largely in phantom lines, a conventional tractor such as may lbe used for the purpose of the invention;
  • FIG. 2 is a side elevational view of the rock ripper and tractor of FIG. l, the tractor again appearing primarily in phantom lines;
  • FIG. 2a is an enlargement of a portion of FIG. 1;
  • FIG. 3 is a rear elevational view of the rock ripper of the invention, looking toward the left in FIG. 2;
  • FIG. 4 is an enlarged side elevational view of a portion of the rock ripper as seen in FIG. 2, portions being broken away to expose underlying structure;
  • FIG. 5 is a section taken on line 5 5 of FIG. 2;
  • FIG. 6 is a longitudinal, vertical and medial sectional view through the rock engaging point, the tooth on the vibratory bar and a fragment of the vibratory bar itself;
  • FIG. 7 is a detail elevational view taken as indicated bythe arrows 7-7 in FIG. 6;
  • FIG. 8 is -a diagrammatic side elevational view of theV vibratory bar of the invention, in typical engagement with a shoulder of bed rock during a ripping operation, and including a standing wave diagram representing the vibratory wave pattern in the bar;
  • FIG. 9 is a view, similar to a portion of FIG. 2, but illustrating a modification of the invention.
  • a suitable tractor is designated generally by the numeral 10, and is of the fairly large type in present use in rock ripping operations where a fixed shank with a ripper point on the lower end thereof is employed.
  • the tractor being conventional, is shown primarily in phantom lines excepting in those parts having direct cooperation or connection with the improvements of the present invention. As indicated, it is typically of a type having crawler tracks 11.
  • Dozer equipment, forming no part of the present invention, is indicated at 14.
  • bracket arms 15 At the rear of the tractor are two vertically disposed, rigidly mounted bracket arms 15, which are spaced from one another laterally of the machine, as clearly appears in FIGS. 1 and 2. As here shown, these bracket arms 15 are connected at their lower ends, as at *16,V to rigid frame bars 17, and at points intermediate thereof, as at 18, to stationary brackets 19 rigidly secured to the rearward end of the tractor. To the lower end portions of these bracket arms 15 are pivotally connected, as at 20, a pair of vertically swingable arms 21, which mount at their rearward or swinging ends a horizontally disposed, transverse tool bar or beam 22 of box section. As indicated, the tool bar .or beam 22 is tted into notches 23 formed in the forward end portions of arms 21, and is securely welded to these arms. Bracing webs 21a are welded between arms 21 and tool bar 22.
  • bracket arms 15 To the upper ends of bracket arms 15 are pivotally connected hydraulic lifting cylinders 24, containing pistons 24a on shafts 25 whose lower ends are pivotally connected to the arms 21 as at 26, as shown best in FIG. 2.
  • the arms 21 have thickened wall portions 2lb which are spaced to provide grooves 21e which receive the lower pivotal end portions of the shafts 25.
  • Shanks 30 Two generally vertically disposed elastically vibratory sonic bars or Shanks 30, bearing rock ripper points P, are employed in the present illustrative equipment, being mounted rearwardly of opposite end portions of the tool bar 22, through mounting arrangements as now to be described.
  • a pair of bar mounting castings 34 are provided, one for each sonic bar or shank 30, and each such casting 34 has a pair of lvertically spaced upper and lower arms 36 and 37, respectively, which t over a pair of bosses formedon the upper and lower plates 32 as shown.
  • a generally vertical pivotal mounting pin 38 extending down through a drill hole 39 in members 36, 32, 37, and the tool bar 22, serves to mount the castings 34 for limited lateral pivot movement on the tool bar 22. As will be seen, the castings 34 are received partially within the notches 33 of the limit plates 32, and their possible moving angles are thereby limited.
  • the rearward end portions of the castings 34 are formed with deep grooves 40, extending generally vertically therethrough, and with the side walls of the grooves in parallel vertical planes longitudinal of the tractor.
  • the aforementioned sonic bars or shanks 30 comprise liat slabs of steel (elastic material of good elastic fatigue properties), of rectangular section, with their flat, vertical sides also in parallel planes longitudinal of the tractor. These bars or shanks 30 are received in the grooves 40, and are spring-urged (biased) toward the bottoms of the grooves, i.e., in the forward direction of the tractor vehicle, by pairs of coil springs 44 received in and between opposed spring-seating cups 45 and 46. The middle portions of forward cups 45 bear against lthe rearward edges of shanks 30.
  • a support plate 48 bears against each rearward cup 46, and long bolts 49 running through lugs 47 on the sides of casting 34, the springs 44, cups 45 and 46, and plate 48, secure the parts in assembly. These parts are further supported by long screws 49a which run through the top part of plate 48, spacer sleeves as indicated, and into lugs 49b on the sides of casting 34.
  • the springs 44 are substantially compressed by the bars 30 because of resistant of the rock being ripped, and the ⁇ bar 30 rides and vibrates at good clearance distance from the bottom of the groove 40, excepting momentarily from time to time as the rock splits or fragments.
  • the springs 44 are tuned to be three-quarters of a wavelength long for the resonant vibration frequency set up as hereinafter described in the shanks or bars 30, so as to substantially isolate the vibration of the bars from the support castings 34. Acoustically speaking, the springs then have high impedance points of zero or minimized vibration amplitude at the support castings, while Vibrating at good amplitude at the opposite ends with the vibration of the bars 30. The springs are thus resonated at the operative frequency of the bars.
  • Each bar 30 has a nodal point mounting at a point which preferably is approximately one-third of its length down from its upper end, so as to 4be at approximately the node N at the one-third point down from the top of a three-quarter wavelength lateral standing wave pattern st (FIG. 8).
  • This mounting for each bar 30 includes a pair of spaced support brackets 50, one on each side of the bar 30, which are mounted on and erected from the corresponding casting 34. Suitable working clearance is provided between the sides of the vibratory bar 30 and brackets, as indicated in FIG. 5.
  • the brackets 50 for each bar are provided at the top, substantially coaxial with the upper nodal point of the bar, with cylindric heads 52 having coaxial bores 53 therethrough. Seated in the bores 53 are short cylinders 55 containing resilient rubber rings 56, preferably bonded therein, which in turn contain and have bonded therein the rim members 57 of hubs 58 which are rotatably.
  • node pin or sleeve 60 mounted on a node pin or sleeve 60 set tightly into a bore 61 formed in the bar 30 concentrically with the top nodal point N of the latter.
  • This preferred mounting will be seen to furnish a resilient support for the node pin 60 and bar 30 near or at the top node of the bar, one-third wavelength distance down from the top, as well as a pivotal support for the bar 30 on the axis of the node pin.
  • the nodal point N of the bar 30 is a point Where the amplitude of standing wave vibration pattern in the bar is minimized, or substantially zero; but there will, in practical situations, still be some small vibration at this node.
  • the resilient rings 56 absorb such vibration and prevent its transmission down the brackets 50 to the casting 34, the tool bar, etc.
  • a vibration or sonic wave generator 64 is rigidly mounted on or in the top end of each bar 30, so as to be acoustically vcoupled to the latter.
  • This vibration generator preferably of a type to be described presently, is driven through a shaft 65 from a uid motor 66.
  • the latter is supported on a mount or carriage 67 which is pivotally mounted on the axis of node pin 60, and is spring urged toward a normal centered position elative to the bar or shank 30.
  • the mount 67 is fastened down to spacers 68 xed to pillow blocks 69 which surround and are supported by the extremities 70 of a shaft 71 that protrudes through sleeve 60.
  • Bushings 69a are used in pillow blocks 69 to afford a rotative fit with shaft extremities 70.
  • Nuts 73 on threaded portions of shaft 70 are set up against end plates 74 for brackets S0, and said end plates 74 engage and close the outer ends of cylindric bracket heads 52.
  • the end plates engage shoulders on enlarged sections 75 of shaft 70, and are clamped thereagainst by setting up the nuts 73.
  • the maximum diameter of shaft 71, at section 75 is afforded good clearance space inside node pin or sleeve 60, so as to avoid vibratory engagement therebetween with any possible vibration of sleeve 60 with the vibratory bar 30, notwithstanding the nodal location of the sleeve 60.
  • the motor 66 and its mount 67 are rotatably mounted about the nodal axis of the bar 30.
  • Motor mount 67 includes a pair of side walls 80 (FIG. 4) which are provided, in alignment with the opposite edges of bar 30, with apertures 81 which receive coil compression springs 82, and the springs 82 seat in cups 83 which are connected and supported against the walls 80 by long bolts 85.
  • the springs 82 bear against the edges of bar 30, above the nodal point or axis N' of the bar 30, ⁇ and act to resiliently or yieldably hold the motor mount 67 centered with bar 30.
  • the springs 82 are preferably onequarter wavelength long (or odd multiple thereof) for the resonant vibration frequency of the system.
  • the upper end portion of the bar 30 can then vibrate laterally about its node point without causing undue vibration of the uid motor.
  • the one-quarter wavelength springs (for the operating frequency of the bar 30) present high impedance at their points of engagement with the motor mount 67, and low impedance at their points of engagement with the laterally vibratory bar 30, and thus serve to isolate the motor mount from the vibration of the bar.
  • the motor thus stands relatively steady while the bar vibrates.
  • the nature of the coupling between the motor and the barmounted generator is such as will readily accommodate the small resulting cyclic misalignment of the axis of the motor relative to the vibration generator.
  • the vibration generator 64 can be any generator which will apply a transversely oriented alternating force of the necessary magnitude to the upper extremity (antinode) of the bar 30. It may also have (but need not have) an alternating force component longitudinal of the bar. For this reason, I can employ some desirable forms of vibratory force generators which generate .a rotating force Vector. In such cases, it is generally only the lateral corn ponent of this force vector that is utilized, because the rotating force vector is caused to turn at a frequency equal to or approximately the resonant frequency for the desired mode of ylateral standing wave vibration in the bar 30. The effect of the longitudinal force component can then be neglected because it does not cause longitudinal resonance.
  • a more sophisticated generator that here indicated, is of a type such as disclosed in several of my copending patent applications, viz, Vibration Generator for Resonant Loads and Sonic Systems Embodying Same, Ser. No. 181,385, new Patent No. 3,217,551, and Sonic Method and Apparatus for Forming Trenches and for Laying Pipe Lines Therein, Ser. No. 258,216, filed Feb. 13, 1963, now Patent No. 3,256,695 which are incorporated herein by this reference.
  • the drive from the motor to the generator is through a conically gyratory shaft, such as the shaft 65 of FIG. 5, which is shown as having a head 88 formed with arcuate splines 89 which mesh will coacting splines 90 inside a drive cup 91 driven from the shaft of fluid motor 66.
  • the opposite end of the conically gyratory shaft 65 drives a rotor mass which rolls around the inside of a raceway in the body of the generator, thus creating a rotating force vector which may be -resolved into two alternating force components actin-g with phase difference therebetween.
  • Generators of the type of that here referred to, as disclosed in said copending applications may also be used in synchronized pairs, so as to balance out the force component longitudinal of the bar, while causing the force components transversely of the bar to be equal and opposite.
  • ywheels side by side, on parallel shafts, geared together to turn in opposite directions at the same speed, and phased so that the eccentrically located centers of gravity of the two fiywheels always move horizontally -in unison, but vertically in opposite directions. An alternating force component will then be generated only horizontally, and not vertically.
  • pairs of the rotor mass generators of the type shown in said copending applications can be used here, by causing them, through simple gearing of their drive shafts, to be similarly phased, so as to generate an alternating force horizontally, or laterally of the bar 30, without a vertical or longitudinal component.
  • the aforementioned applications should be consulted.
  • the vibration generators 64 here shown have cylindrical housings 95 and are fixed to the upper extremities of bars or shanks 30 by installation in apertures 96 formed in the shanks 39 near the tops of the latter.
  • the upper ends of the Shanks are split down into the apertures 96, as at 97, and clamp bolts 98 extending transversely through the bars, across the splits 97, are set up tight to hold the generators rigidly in place in the upper extremities of the shanks 30, and thus acoustically coupled thereto.
  • each shank 30 is shown in a typical form in FIGS. 6 and 7.
  • This structure as here shown is substantially as heretofore utilized in non-vibratory rock ripping, and involves no novelty per se.
  • the point P as usual, has a socket 99 which receives a tooth 99a welded to the lower end portion of the bar 30 at or ladjacent the lower end of the latter, and the point P is connected to the tooth 99a by a removable pin 100.
  • the hydraulic cylinders 24 and the uid motor 64 for the vibration generators are powered by hydraulic fluid from pumps 104 and 105 (FIG. l) driven from power take-01T shafts 106 leading through suitable transmission means, not shown, from the engines of the tractor.
  • the pumps 104 and 105 are shown positioned inside reservoir tanks 106 and 107, respectively, and the pumps take the hydraulic Huid, preferably oil, directly from the reservoir.
  • the pump is a dual pump, and has two outlets 108 and 109 which pump hydraulic uid via flexible hoses 110 and 111, respectively, to the two fluid motors 66 associated with the vibration generators for the two vibratory bars or shanks 30.
  • Flexible return hoses 112 land 113 return the exhaust fluid to the reservoir.
  • By-pass valves C are connected between each pair of lines 110, 112 and 111, 113 and are used when the pump 105 is in operation, to lfeed the hydraulic pressure uid either through the hydraulic motors 66 to drive the oscillators at maximum effort, or to return it partially or wholly to the reservoir.
  • These valves are indicated only diagrammatically in FIG. l, and for convenience of illustration, have been shown out at the uid motors. It will be understood that in practice they will more conveniently be located back in the area of the pump or reservoir, and will have control means, not
  • the other pump 104 is connected through suitable conventional control valve means, not shown, to feed hydraulic liuid via hoses 116 to or from the lower ends of hydraulic elevator cylinders 112, and via hoses 117 to or from the upper ends of said cylinders 112, for elevation of the tool bar 22 and equipment carried thereby, in order to raise the lower end of the shanks 30 to an inoperative carrying position or to drop them to a selected working position such as indicated in FIG. 8.
  • a typical performance may be achieved such as represented in the standing wave diagram st of FIG. 8, where the horizontal width between the lines represents the lateral vibration amplitude of the bar at corresponding points along the latter.
  • a bottom node N appears a short fraction of a wavelength distance above the lower extremity of the bar, i.e., above the point. At the lower extremity, and therefore at the point, a small vibration amplitude is displayed.
  • the modification is accomplished through the tendency ofthe relatively sharp wedge-shaped point to embed itself in the rock, by high bias force (draw bar pull at node N', or draw bar push on the lower region of the back edge of bar 30) and is aided also by the location of the upper mounting for the bar at a location approximately one-third the length of the bar down from the upper end.
  • the vibrations of the point, the bias force, and the radiated sonic vibrations all have substantial or predominating components which are, in general, parallel to the top surface of the rock.
  • the rock, so treated, fails and literally flys apart along -fracture lines or planes located ahead of the point.
  • the vibrating point engaging or wedging into the rock, actually places the rock in cyclic tension transversely across the medial plane of the point, tending toward both simply pulling the rockV apart, and also leading to fatigue failure of the rock.
  • the operator may occasionally, during the vibratory action, suddenly pull up on the points by means of the hydraulic lift cylinders, which sometimes, under the prevailing conditions of vibratory action, results in instantaneous fracturing a substantial quantity of the rock.
  • the function of the Vertical pivotal mountings of the bar support casting 34 is to permit free lateral swinging movement of the castings 34 and bars 30 as the tractor turns, so as to avoid overstressing side loads between the vibrating bars 30 and the opposed guide surfaces in the castings 34 under these conditions.
  • FIG. 9 shows a modified mounting of the tool bar from the tractor, involving a parallel linkage which maintains the vibratory point-carrying shanks in a predetermined orientation, preferably approximately normal to the longitudinal direction of the tractor, regardless of how positioned by the elevator.
  • the tractor is designated at 130, and carries at the rear vertical bracket arms 131, suspending hydraulic cylinder elevator means 132, pivotally linked as at 133 to tool bar 134.
  • the latter may be the same in general respects as the bar 22 of FIGS. l and 2.
  • Welded to the top and bottom of tool bar 134 are plates 136 and 137, understood to be notched out to the rear the same as the limit plates 32 of FIGS. l and 2, but extended forwardly from the tool bar to afford pivot mountings for the shank support castings 138.
  • pivot pins 139 pivotally mount the arms 140 and 141 of castings 138 on plates 136 and 137.
  • the tool bar 134 has upper and lower ears 146 and 147, which are pivotally connected at 148 and 149 to upper and lower link arms 150 and 151, respectively, which arms are pivotally mounted at 152 and 153, respectively, to brackets 154 secured in any way to the main frame of the tractor.
  • the casting 138 of which there may be two, as in FIGS. 1 and 2, has associated therewith a normally approximately vertically disposed vibratory shank 160, carrying a point 161, and excepting for the mounting arrangements for the casting 138, said casting, the shank 160, the spring-bias means 162, the nodal mounting 163 for the shank, the vibration generator 164, and the fluid motor 165, may all be like the corresponding components more particularly illustrated in FIGS. l to 8.
  • the parallel linkage mounting arrangement for the tool bar in FIG. 9 is such that the directional orientation of the vibratory bar 160 relative to the tractor is undisturbed as the tool bar 134 is raised or lowered by the elevating means 132.
  • a sonically vibratory rock ripping machine comprising:
  • an elongated elastic bar mounted on said vehicle so as to extend generally vertically and transversely of the direction of said forward thrust, and so as to have upper and lower ends, said bar being elastically vibratory at a resonant frequency in a wave pattern characterized by a lateral mode of standing wave vibration in a vertical plane parallel to said direction of forward thrust, with at least one nodal point between its upper and lower ends, at least one velocity antinode therealong, and with a vibratory portion at its lower end,
  • bar supporting means on said vehicle including a bar mounting affording support for said bar and through which the forward thrust of said vehicle is applied to said bar, and
  • a vibration generator for vibrating said bar at said resonant frequency coupled to said bar in a region of substantial vibration amplitude thereof and being arranged for application to said bar of a cyclic force which has a substantial component laterally of said bar.
  • said bar supporting means includes means for lowering and elevating said bar relative to said vehicle between positions above and below the surface being traversed by the vehicle.
  • said generator is of the orbital mass rotor type, including a drive shaft disposed along a drive axis parallel to said nodal point axis,
  • a iluid drive motor for said vibration generator having a drive shaft on said drive axis coupled to said drive shaft of said generator
  • exible hoses connecting said source and reservoir with said fluid motor, said hoses affording freedom for vibration and of pivotal swinging movement of said bar on said nodal axis.
  • said bar supporting means includes a pivot joint affording a limited freedom for lateral swinging action of said bar mounting and bar.
  • said elongated elastic bar is wider than it is thick, so as to have relatively wide side surfaces, and is oriented on the vehicle with its wide side surfaces in planar, substantially parallel relationship with the direction of travel ofthe vehicle.
  • vibration generator is rigidly mounted on said bar adjacent the upper end of the latter, said generator being of the orbital mass rotor type.
  • said generator includes a drive shaft disposed along a drive axis parallel to said nodal point axis,
  • a drive motor for said vibration generator having a drive shaft on said drive axis coupled to said drive shaft of said generator
  • a sonically vibratory rock ripping machine comprising:
  • an elongated elastic bar mounted on said vehicle so as to extend vertically and transversely of the direction of said forward thrust, and so as to have upper and lower ends, said bar being elastically vibratory at a resonant frequency in a wave pattern characterized by a lateral mode of standing wave vibration in a vertical plane parallel to said direction of forward thrust, with at least one nodal point between its upper and lower ends, at least one velocity antinode therealong, and with a vibratory portion at its lower end,
  • bar supporting means on said vehicle including a bar mounting affording support for said bar about a nodal point axis transverse to the bar and substantially through said nodal point, and through which the forward thrust of said vehicle is applied to said bar,
  • a vibration generator for vibrating said bar at said resonant frequency coupled to said bar in a region of substantial vibration amplitude thereof and being arranged for application to said bar of a cyclic force which has a substantial component laterally of said bar.
  • said spring means is tuned to resonate at the resonant operating frequency of the vibratory bar, so as to present a low impedance at the bar and a high impedance at the vehicle.
  • said bar mounting supports said bar at a point spaced generally one-third of the length of the bar down from its upper end, said .bar mounting and said ripper point being so located relative to said bar that, with said point in tight rock engagement, said standing wave for resonance is characterized by the location of said nodal point at said bar mounting, the provision of a second nodal point shortly above the lower end of said bar, and a rudimentary antinode at the lower extremity of the bar.
  • said bar mounting pivotally supports said bar at a point spaced substantially one-third of the length of the bar down from its upper end, and wherein said spring means acts on said bar in the direction of said forward thrust at a vibratory point of said bar below the pivotal support of the bar.
  • a sonic radiator point which is on the lower end of an elongated, elastic, generally vertically disposed bar having a pivotal mounting in an upper region thereof,

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  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Soil Working Implements (AREA)
  • Medicines That Contain Protein Lipid Enzymes And Other Medicines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
US402136A 1964-10-07 1964-10-07 Method and apparatus for ripping rock by sonically vibratory teeth Expired - Lifetime US3336082A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US402136A US3336082A (en) 1964-10-07 1964-10-07 Method and apparatus for ripping rock by sonically vibratory teeth
GB38437/65A GB1096850A (en) 1964-10-07 1965-09-08 Method and apparatus for ripping rock
JP40059198A JPS4821241B1 (enrdf_load_stackoverflow) 1964-10-07 1965-09-29
DE19651634705 DE1634705A1 (de) 1964-10-07 1965-10-01 Maschine und Verfahren zum Brechen bzw.Aufreissen von Gestein durch Schallschwingungen

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US402136A US3336082A (en) 1964-10-07 1964-10-07 Method and apparatus for ripping rock by sonically vibratory teeth

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US (1) US3336082A (enrdf_load_stackoverflow)
JP (1) JPS4821241B1 (enrdf_load_stackoverflow)
DE (1) DE1634705A1 (enrdf_load_stackoverflow)
GB (1) GB1096850A (enrdf_load_stackoverflow)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3437381A (en) * 1968-02-05 1969-04-08 Albert G Bodine Vehicle mounted sonic shearing device having propulsion aiding means
US3457660A (en) * 1966-09-01 1969-07-29 Martin J Speno Ballast undercutting mechanism
US3461971A (en) * 1966-07-05 1969-08-19 American Tractor Equip Corp Vyba mount
US3561539A (en) * 1968-05-09 1971-02-09 Universal Vibro Inc Vibratory ripper plow
US3575006A (en) * 1968-09-20 1971-04-13 Tel E Elect Inc Underground cable-laying apparatus
US3746100A (en) * 1971-11-12 1973-07-17 Charles Machine Works Mounting for vibrating tool having damping means for isolating vibrations
US4067369A (en) * 1976-01-05 1978-01-10 Weyerhaeuser Company Whole tree extraction device
US4102403A (en) * 1976-10-15 1978-07-25 Vibra-King, Inc. Apparatus for making a slit trench
US4141398A (en) * 1974-11-27 1979-02-27 Firma Elektro-Diesel Method and apparatus for severing tree roots and felling trees
WO1979000563A1 (en) * 1978-01-30 1979-08-23 Gurries Co Pavement planing method and apparatus
WO1980001637A1 (en) * 1979-02-12 1980-08-21 Caterpillar Tractor Co Impact ripper
US4229044A (en) * 1979-02-12 1980-10-21 Caterpillar Tractor Co. Clevis-mounted impact ripper
US4330156A (en) * 1980-03-14 1982-05-18 Resonant Technology Co. Resonant system speed control
US4436452A (en) 1982-07-12 1984-03-13 Bodine Albert G Sonic pile driver system employing resonant drive member and phased coupling
US4515408A (en) * 1981-12-10 1985-05-07 Resonant Technology Company Counterweight support for resonantly driven tool
US4605089A (en) * 1983-06-03 1986-08-12 Spetsialnoe Proektno-Konstruktorskoe I Tekhnologicheskoe Bjuro Po Pogruzhnomu Elektrooborudovaniju Dlya Burenia Skvazhin I Dobychi Nefti Vnpo "Potentsial" Method of and apparatus for generating shear seismic waves
US20090127918A1 (en) * 2005-03-23 2009-05-21 Longyear Tm, Inc. Vibratory milling machine having linear reciprocating motion
US20110036630A1 (en) * 2005-03-23 2011-02-17 Boart Longyear Inc. Vibratory drilling machine
US20180179729A1 (en) * 2016-12-28 2018-06-28 Cnh Industrial America Llc Accessory mounting system for a work vehicle
CN113006732A (zh) * 2021-02-26 2021-06-22 河北华北石油荣盛机械制造有限公司 一种水下设备储能控制装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50111624A (enrdf_load_stackoverflow) * 1974-02-13 1975-09-02
JPS5142125A (ja) * 1974-10-07 1976-04-09 Iwao Nakajima Gasuanzensochi
JPS5142123A (ja) * 1974-10-07 1976-04-09 Masaru Iwai Gasuanzensochi

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB519046A (en) * 1937-09-13 1940-03-14 Hermes Patentverwertungs Gmbh Improvements in or relating to machines for the treatment of the ground, such as agricultural implements, for instance ploughs, harrows and the like
US2670943A (en) * 1949-03-26 1954-03-02 Mavor & Coulson Ltd Mining machine
US3030715A (en) * 1959-09-10 1962-04-24 Albert G Bodine Sonic wave earth digging and moving machines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB519046A (en) * 1937-09-13 1940-03-14 Hermes Patentverwertungs Gmbh Improvements in or relating to machines for the treatment of the ground, such as agricultural implements, for instance ploughs, harrows and the like
US2670943A (en) * 1949-03-26 1954-03-02 Mavor & Coulson Ltd Mining machine
US3030715A (en) * 1959-09-10 1962-04-24 Albert G Bodine Sonic wave earth digging and moving machines

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3461971A (en) * 1966-07-05 1969-08-19 American Tractor Equip Corp Vyba mount
US3457660A (en) * 1966-09-01 1969-07-29 Martin J Speno Ballast undercutting mechanism
US3437381A (en) * 1968-02-05 1969-04-08 Albert G Bodine Vehicle mounted sonic shearing device having propulsion aiding means
US3561539A (en) * 1968-05-09 1971-02-09 Universal Vibro Inc Vibratory ripper plow
US3575006A (en) * 1968-09-20 1971-04-13 Tel E Elect Inc Underground cable-laying apparatus
US3746100A (en) * 1971-11-12 1973-07-17 Charles Machine Works Mounting for vibrating tool having damping means for isolating vibrations
US4141398A (en) * 1974-11-27 1979-02-27 Firma Elektro-Diesel Method and apparatus for severing tree roots and felling trees
US4067369A (en) * 1976-01-05 1978-01-10 Weyerhaeuser Company Whole tree extraction device
US4102403A (en) * 1976-10-15 1978-07-25 Vibra-King, Inc. Apparatus for making a slit trench
WO1979000563A1 (en) * 1978-01-30 1979-08-23 Gurries Co Pavement planing method and apparatus
WO1980001637A1 (en) * 1979-02-12 1980-08-21 Caterpillar Tractor Co Impact ripper
US4229044A (en) * 1979-02-12 1980-10-21 Caterpillar Tractor Co. Clevis-mounted impact ripper
US4330156A (en) * 1980-03-14 1982-05-18 Resonant Technology Co. Resonant system speed control
US4515408A (en) * 1981-12-10 1985-05-07 Resonant Technology Company Counterweight support for resonantly driven tool
US4436452A (en) 1982-07-12 1984-03-13 Bodine Albert G Sonic pile driver system employing resonant drive member and phased coupling
US4605089A (en) * 1983-06-03 1986-08-12 Spetsialnoe Proektno-Konstruktorskoe I Tekhnologicheskoe Bjuro Po Pogruzhnomu Elektrooborudovaniju Dlya Burenia Skvazhin I Dobychi Nefti Vnpo "Potentsial" Method of and apparatus for generating shear seismic waves
US20090127918A1 (en) * 2005-03-23 2009-05-21 Longyear Tm, Inc. Vibratory milling machine having linear reciprocating motion
US20110036630A1 (en) * 2005-03-23 2011-02-17 Boart Longyear Inc. Vibratory drilling machine
US8056985B2 (en) 2005-03-23 2011-11-15 Longyear Tm, Inc. Vibratory machine
US8079647B2 (en) * 2005-03-23 2011-12-20 Longyear Tm, Inc. Vibratory milling machine having linear reciprocating motion
US20180179729A1 (en) * 2016-12-28 2018-06-28 Cnh Industrial America Llc Accessory mounting system for a work vehicle
US11306459B2 (en) * 2016-12-28 2022-04-19 Cnh Industrial America Llc Accessory mounting system for a work vehicle
CN113006732A (zh) * 2021-02-26 2021-06-22 河北华北石油荣盛机械制造有限公司 一种水下设备储能控制装置

Also Published As

Publication number Publication date
JPS4821241B1 (enrdf_load_stackoverflow) 1973-06-27
DE1634705A1 (de) 1970-07-16
GB1096850A (en) 1967-12-29

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